FR2612430A1 - Pressure treatment cylinder, in particular for calanders and laminoirs - Google Patents

Pressure treatment cylinder, in particular for calanders and laminoirs Download PDF

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Publication number
FR2612430A1
FR2612430A1 FR8807030A FR8807030A FR2612430A1 FR 2612430 A1 FR2612430 A1 FR 2612430A1 FR 8807030 A FR8807030 A FR 8807030A FR 8807030 A FR8807030 A FR 8807030A FR 2612430 A1 FR2612430 A1 FR 2612430A1
Authority
FR
France
Prior art keywords
bearing
cylinder
bearing element
pressure
casing
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
FR8807030A
Other languages
French (fr)
Other versions
FR2612430B1 (en
Inventor
Josef Pav
Reinhard Wenzel
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Kleinewefers GmbH
Original Assignee
Kleinewefers GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority to DE3325385A priority Critical patent/DE3325385C2/de
Application filed by Kleinewefers GmbH filed Critical Kleinewefers GmbH
Publication of FR2612430A1 publication Critical patent/FR2612430A1/en
Application granted granted Critical
Publication of FR2612430B1 publication Critical patent/FR2612430B1/en
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

Links

Classifications

    • BPERFORMING OPERATIONS; TRANSPORTING
    • B21MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21BROLLING OF METAL
    • B21B27/00Rolls, roll alloys or roll fabrication; Lubricating, cooling or heating rolls while in use
    • B21B27/02Shape or construction of rolls
    • B21B27/03Sleeved rolls
    • B21B27/05Sleeved rolls with deflectable sleeves
    • B21B27/055Sleeved rolls with deflectable sleeves with sleeves radially deflectable on a stationary beam by means of hydraulic supports
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16CSHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C13/00Rolls, drums, discs, or the like; Bearings or mountings therefor
    • F16C13/02Bearings
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16CSHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C13/00Rolls, drums, discs, or the like; Bearings or mountings therefor
    • F16C13/02Bearings
    • F16C13/022Bearings supporting a hollow roll mantle rotating with respect to a yoke or axle
    • F16C13/024Bearings supporting a hollow roll mantle rotating with respect to a yoke or axle adjustable for positioning, e.g. radial movable bearings for controlling the deflection along the length of the roll mantle
    • F16C13/026Bearings supporting a hollow roll mantle rotating with respect to a yoke or axle adjustable for positioning, e.g. radial movable bearings for controlling the deflection along the length of the roll mantle by fluid pressure
    • F16C13/028Bearings supporting a hollow roll mantle rotating with respect to a yoke or axle adjustable for positioning, e.g. radial movable bearings for controlling the deflection along the length of the roll mantle by fluid pressure with a plurality of supports along the length of the roll mantle, e.g. hydraulic jacks
    • BPERFORMING OPERATIONS; TRANSPORTING
    • B29WORKING OF PLASTICS; WORKING OF SUBSTANCES IN A PLASTIC STATE IN GENERAL
    • B29CSHAPING OR JOINING OF PLASTICS; SHAPING OF MATERIAL IN A PLASTIC STATE, NOT OTHERWISE PROVIDED FOR; AFTER-TREATMENT OF THE SHAPED PRODUCTS, e.g. REPAIRING
    • B29C43/00Compression moulding, i.e. applying external pressure to flow the moulding material; Apparatus therefor
    • B29C43/32Component parts, details or accessories; Auxiliary operations
    • B29C43/44Compression means for making articles of indefinite length
    • B29C43/46Rollers

Abstract

<P> THE PRESENT INVENTION CONCERNS A PRESSURE TREATMENT CYLINDER. </ P> <P> THE PURPOSE OF THE INVENTION IS TO CREATE SUCH A CYLINDER HAVING EASY ACCESS BEARING UNITS. </ P> <P> THIS PURPOSE IS REACHED WITH A PRESSURE TREATMENT CYLINDER 1 COMPRISING AN ENVELOPE 3 WHICH IS CROSSED BY A FIXED SUPPORT 4 BASED ON ITS ENDS IN A CAGE, EACH END OF THE ENVELOPE COMPRISING A BEARING UNIT 522 INCLUDING THE OUTDOOR BEARING ELEMENT 523 TURNS WITH THE ENCLOSURE OF THE CYLINDER AND WHICH THE INNER BEARING ELEMENT 524 COOPERS WITH SOLIDARITY ELEMENTS OF THE SUPPORT FOR ABSORBING THE AXIAL FORCES AND ENSURING SEALING, CHARACTERIZED IN THAT THE BEARING ELEMENT EXTERIOR 523 IS HYDRAUSSTICALLY MOUNTED ON THE SIDE SURFACE OF THE INNER BEARING ELEMENT 524. </ P> <P> SUCH CYLINDERS ARE SUITABLE IN PARTICULAR FOR CALENDERS OR ROLLING MILLS. </ P>

Description

PRESSURE TREATMENT CYLINDER, IN PARTICULAR

FOR CALENDAR AND LAMINOIRS ".

  The subject of the invention is a pressure treatment cylinder comprising a casing which is traversed by a fixed support resting at its ends in a cage and which is mounted on bearing elements acting on bearing sections distributed over the length of the envelope and. loaded by hydraulic pressure members, these elements pressing the envelope -du cylinder vis-a-vis at least one other cylinder, each end of the casing having a bearing unit whose outer bearing element rotates with the casing of the cylinder, and whose inner bearing element cooperates with elements integral with the support to absorb axial forces and / or to seal in which in particular, the casing of the cylinder and with it, the Bearing unit are movable. Such processing cylinders are suitable for many applications, for example for calenders, calendering machines, paper machine compression parts, pulp machines and printing machines or rolling mills for steel,

  plastics and similar materials.

  In a known pressure treatment cylinder of this type (British Patent 641,466), each of the support elements is constituted by the front face of the piston of the hydraulic pressure members provided in the pressure treatment plane in a row directed towards the other cylinder. By an appropriate pressure load of the pressure members, it is possible to obtain a

  lifting and applying movement of the screw envelope

  opposite the neighboring cylinder. The bearing unit comprises an outer bearing element assembled with the casing and an inner bearing element, between which is a rolling bearing ring. By means of this bearing unit, the axial components of the forces of the envelope can be transmitted to the support. When the pressure sent to the pressure members is cut off, the inner bearing element acts as a stop which limits the possibility of radial displacement of the cylinder casing. In addition, the bearing unit serves, in conjunction with sealing elements, to seal against the outside of the interior volume of the housing.

the cylinder envelope.

  Furthermore, a pressure treatment cylinder (German Patent No. 29 42 002) is known in which the bearing elements which are each loaded by two or more pressure members offset in the peripheral direction have hydrostatic bearing surface. Such bearing elements may also be provided on opposite sides two to

two of the support.

  The object of the invention is to create a pressure treatment cylinder of the type described in the preamble,

  and having easy access bearing units.

  For this purpose, the invention relates to a cylinder of the above type characterized in that the outer bearing element is mounted hydrostatically on the

  lateral surface of the inner bearing element.

  It is also recommended that the end faces for transmitting axial forces from the outer bearing element to the bearing element

  inside form hydrostatic bearings.

  Thus, a low friction is also obtained on the end faces, and the torques transmitted by these front faces are maintained at

low values. -

  The inner bearing element can thus maintain its relative position relative to the support. It is also possible to freely adjust the angular position of

the axis of the cylinder.

  The invention will be better understood with regard to the

  description below and accompanying drawings showing

  preferred embodiments, drawings in which: - Figure 1 is a partial longitudinal section of a pressure treatment cylinder according to the invention - Figure 2 is a cross section taken along the line AA of Figure 1 FIG. 3 is a cross-section taken along line BB of FIG. 1; FIG. 4 is a partial longitudinal section of a second exemplary embodiment; FIG. 5 is a cross-section taken along the line CC of FIG. FIG. 4; FIG. 6 is a partial longitudinal section of a third exemplary embodiment; FIG. 7 is a cross-section taken along the line DD of FIG. 6; FIG. 8 is a partial longitudinal section of FIG. a fourth exemplary embodiment, - Figure 9 is a cross section taken along the line EE of Figure 8, - Figure 10 is a partial longitudinal section of a fifth embodiment, FIG. 11 is a cross-section taken along the line FF of FIG. 10, FIG. 12 is a partial longitudinal section of a sixth embodiment, FIG. 13 is a cross-section of an exemplary embodiment in FIG. wherein the pressure treatment plane is at an angle to the vertical, FIG. 14 is a cross-section of a variant embodiment in the embodiment of FIG. 13, FIG.

  exemplary embodiment with two antagonistic cylinders.

  Figures 1 & 3 show a pressure treatment cylinder 1 which cooperates with a cylinder

antagonist 2.

  The pressure treatment cylinder 1 comprises a hollow cylindrical envelope 3 traversed by a support 4. This support is, at its two ends, held in a cage 6, without the possibility of rotation,

by means of a pivoting support 5.

  Supporting elements 8 and 9 act on opposite sides of the support 4 on bearing sections 7 located axially adjacent to each other on the inner side surface of the casing 3. As shown in FIG. 2, each support element is loaded by two pressure members 10, 11 and 12, 13. Each pressure member comprises a piston 14 fixed to the support and a cylinder 15 formed on the support element. . The pressure chamber 16 thus formed is connected on the one hand by a radial duct 17 and an axial duct 18 with a pressure regulator 19 fed by a pump and on the other hand via a duct 20, with a bearing housing 21 forming part of a hydrostatic bearing formed on the surface of the

the support element 8, 9.

  Each end of the envelope 3 comprises a bearing unit 22 comprising an outer bearing element 23 formed by the end of the cylinder and a

  inner bearing element 24 in the form of a pad.

  Between these elements is disposed a rolling bearing 25 whose rings are fixed to the inner bearing element and the outer bearing element by end stops, for example by the stop ring 26, of 3i

  to allow the transmission of axial forces.

  The rolling bearing 25 is provided externally with a seal 27. The inner bearing element carries on its front side a sealing ring 28 which bears against a plate 29 held without the possibility of rotation on the support 4 The axial position of the inner bearing element 24 is fixed by a shoulder 30 of the support 4 and by a stop ring 31.

acting on the plate 29.

  A game 32 is provided between the inner bearing element 24 and the support 4, this game allowing the free

  movement of the end of the envelope.

  The lowest position is obtained when the inner bearing member 24 comes against the support 4, which occurs when no pressure is sent to the pressure members. The exact position of the bearing unit 22 is determined by means of three position sensors 33, 34 and 35 which determine the relative position of the inner bearing member 24 with respect to the portion 36 of the support 4. The The sensor 35 measures the position difference Ay in the direction of the pressure treatment plane 37. The sensors 33 and 34 measure the differences AX1, AX2 from the pressure treatment plane. As position sensors, it is possible to use sensors of known mechanical, electrical, optical, pneumatic and hydraulic type as well as

  other stroke or position sensors.

  The values measured by the sensors are sent to a computer 38 which has inputs 39 by which signals can be introduced, for example the output signals of pressure or force sensors arranged in each part of the envelope 3 to control the balance of forces and which determine the load of that part of the envelope or sensors that determine the properties of the strip product. It is also possible to introduce at this location linear load reference values or programs which take into account a large number of different parameters. This computer 38 controls the pressure regulator 19 as a function of the values determined by the sensors and of the process parameters of the D cylinder system (for example the cylinder temperature profile) after comparison with setpoint values.

  predetermined or with a predetermined program.

  The control takes place so as to send to the pressure chamber 16 of each pressure member a pressure such that the desired linear load is established in the gap 40, that the envelope 3 takes a predetermined shape in the direction of the plane pressure treatment 37 as well as perpendicular to this plane and that the axis of the envelope is maintained in the pressure treatment plane 37 despite the action of external transverse forces. It is then necessary, to develop the transverse force components, to send different pressures to the two pressure members of each support element. Furthermore, in order to achieve the appropriate relationship between the force components which are located in the pressure treatment plane and the perpendicularly extending force components, it is necessary to send the pressure member to the pressure members. higher 8 higher pressure than the pressure members of the lower support member 9. It can also meet several adjacent pressure members in the axial direction

  and feed them through a common pressure line.

  Instead of the two pressure members shown, three pressure members or a larger number of

  pressure can also act on a support element.

  Thus, the cylinder casing is worn

  exclusively by the hydrostatic support elements.

  The load-bearing forces and the stabilizing forces necessary to develop the linear load and the stabilization of the position of the envelope are applied solely by the pressure members. This action of the forces is exactly predetermined by the control of the pressure regulator 19. The stresses are eliminated substantially completely at the ends of the envelope. The ends of the envelope, including the bearing units 22, are held in their median position by compensation of the transverse forces. Due to the low friction between the sealing ring 28 and the plate 29, rotation of the inner bearing member 24 is avoided. As a result, the movement of the cylinder axis takes place substantially unhindered in the pressure treatment plane 37. The materials of the inner bearing member 24 and the plate 29 do not have to present the

  properties required for a sliding bearing.

  When the rolls are united, the position of the envelope 3 can also be determined directly with respect to the counter-roll 2. The determination of the position and the control of the parallelism of the generatrices during the formation of the interval can be carried out using position sensors known per se. In the exemplary embodiment according to FIG. 4 and FIG. 5, the same reference numerals are used for identical elements and, for corresponding elements, reference numerals

  increased by 100 compared to those of Figures 1 to 3.

  On the front face 41 of the inner bearing elements 124 directed towards the pressure sensors, a diametrical groove 42 is formed which extends into a collar 43 which goes close to the casing 3. In this collar, a support of torque 44, 45 is disposed on each side of the support 4, this torque support being in the form of a rotating roller. Each torque support is held with clearance between two opposing surfaces 46, 47 formed by the side walls of the groove 42 which extend parallel to the pressure treatment plane 37 connecting the axes of the two cylinders 1 and 2 and passing through the 39 interval formed between the cylinders. The torque supports 44, 45 are

  mounted to rotate on a retainer 48.

  The displacement of the envelope 3 in the direction of the pressure treatment plane 37 is possible to the full extent of the clearance 32 and, in the transverse direction, at least in the context of the clearance that remains between the torque supports 44, 45. and the two opposing surfaces 46, 47 as long as the retaining member 48 is not itself elastically deformable to a certain extent. The rotation of the inner bearing element 124 is prevented by the torque supports 44, 45. Since these only apply with a small force on the opposing surfaces, the bearing also takes place with a low friction, the displacement of the axis of the cylinder in the treatment plane by

  pressure 37 is performed without hindrance.

  In the exemplary embodiment according to FIG. 6 and FIG. 7, the same reference numerals are used for identical elements and, for corresponding elements, numerical references

  increased by 200 compared with those of Figures 1 to 3.

  Pressings of axial forces 50, 51 in the form of pairs of rollers, are arranged on a retaining member 148, these supports cooperating with a surface

  antagonist 52 of the inner bearing member 224.

  In addition, axial force supports 53, 54 in the form of pairs of rollers are arranged on this bearing element, these supports cooperating with an opposing surface 55 of the plate 29. Consequently, axial components can be transmitted. larger envelope 3 to the support 4, without the casing 3 is exposed to friction forces uncontrolled in the pressure treatment plane 37

in case of radial movement.

  In the exemplary embodiment according to FIG. 8 and FIG. 9, the same reference numerals are used for identical elements and, for corresponding elements, numerical references

  D5 increased by 300 compared with those of Figures 1 to 3.

  The torque support 344, in the form of a roller, is arranged only on one side of the support 4, with a clearance between opposing surfaces 346, 347 formed by the side walls of a groove 342 extending from the face end. 348 fork-shaped bracket, recessed

  in the support 4, serves to maintain the roller.

  In the exemplary embodiment according to the figure and FIG. 11, the same reference numerals are used for identical elements and, for corresponding elements, numerical references

  increased by 400 compared with those of Figures 1 to 3.

  Torque bearings 444 and 445 are disposed on the inner bearing member 424, with clearance between

  antagonistic surfaces 446, 447 provided on the cage 406.

  In this case, the plate 429 has a smaller diameter and the bearing member 424 carries the seal 428

  on a flange 60 advancing inwards.

  In the embodiment of Figure 12, it is not necessary to provide torque supports because of the ease of movement of the hydrostatic bearing unit 422. This construction is a variant of the bearing unit 22 of Figure 1. For identical elements, the same reference numerals are used and, for corresponding elements, numerical references increased by 500 relative to those of Figures 1 to 3. The outer bearing element 523 is constituted by two bearing rings 61, 62 which rest one on the other by a spherical surface 63,

  to form a ball joint.

  The inner bearing member 524 has a hydrostatic bearing surface 64 on which the inner ring 62 of the outer bearing member 523 is mounted. On either side of this inner ring 62 are front bearing surfaces 65 , 66 which are also arranged to act hydrostatically. Suitable oil lines 67 feed this hydrostatic bearing to allow operation with a

low friction.

  In the case of Figure 13, the envelope carries an elastic coating 68, for example paper. This figure shows that the cylinders 1 and 2 are not necessarily arranged vertically one above the other, but that the pressure treatment plane 37 can also make an angle with the vertical. In this case, the weight G of the envelope 3 already acts so that there is a transverse force component Q in addition to the force component P which passes into the pressure treatment plane. It is then necessary that the pressures sent to the pressure members 11 and 13 are greater than the pressures sent to the pressure members 10 and 12 so that the transverse force component Q is compensated. If additional transverse forces are still established in service, the pressures to be sent to the pressure

  should be modified accordingly.

  FIG. 14 represents a variant of FIG. 13. For identical elements, the same reference numerals are used and for corresponding elements, the reference numerals are increased by 600 relative to those of FIGS. 1 to 3. The support 604 has a section substantially triangular. In the zone of each supporting section 7, three bearing elements 608, 70, and 71 are provided. By means of the supporting elements 71 provided outside the pressure treatment plane 37, it is possible to apply components relatively large transverse forces without the need to simultaneously produce high force components in the direction of the pressure treatment plane. Figure 15 shows that cylinder 1 can

  > also cooperate with two antagonist cylinders 2 and 602.

  In this case, one, 608, support members may be adjustable in the direction of one, 37, pressure treatment planes and the second support member 70 may be adjustable in the direction of the other plan of

pressure treatment 637.

Claims (4)

  1) a pressure treatment cylinder (1) comprising a casing (3) which is traversed by a fixed support (4) resting at its ends in a cage and which is mounted on bearing elements (8, 9, 608, 71) acting on bearing sections (7) distributed over the length of the casing and loaded by hydraulic pressure members (10, 11, 12, 13), these elements supporting the casing of the cylinder at least one other cylinder, each end of the casing having a bearing unit (22) whose outer bearing element rotates with the casing of the cylinder and whose inner bearing element cooperates with elements integral with the support for absorbing axial forces and / or for sealing, in which, in particular, the casing of the cylinder and with it the bearing unit are displaceable, characterized in that the bearing element outside (523) is mounted hydrostatically on the lateral surface of the element of
inner bearing (524).
  2) Pressure treating cylinder according to claim 1, characterized in that the end faces (65, 66) for transmitting axial forces of the outer bearing element (523) to the inner bearing element (524). also form
hydrostatic bearings.
  Pressure control cylinder according to claim 1 or 2, characterized in that the hydrostatic bearing surfaces (64, 65, 66) are formed on
the inner bearing element.
  4) Pressure Cylinder according to
  any of claims 1 to 3, characterized in that
  the outer bearing element (523) is constituted by two bearing rings (61, 62) which rest on one another by a spherical surface (63) to form a ball joint, and in that the inner bearing ring (62) is mounted on the hydrostatic bearing surface (64) of the inner bearing member
(524).
FR8807030A 1983-07-14 1988-05-26 Pressure processing cylinder, especially for calenders and rolling mills Expired - Fee Related FR2612430B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE3325385A DE3325385C2 (en) 1983-07-14 1983-07-14

Publications (2)

Publication Number Publication Date
FR2612430A1 true FR2612430A1 (en) 1988-09-23
FR2612430B1 FR2612430B1 (en) 1993-10-08

Family

ID=6203956

Family Applications (2)

Application Number Title Priority Date Filing Date
FR8411041A Pending FR2548929A1 (en) 1983-07-14 1984-07-11 Pressure treatment cylinder, in particular for calanders and laminoirs
FR8807030A Expired - Fee Related FR2612430B1 (en) 1983-07-14 1988-05-26 Pressure processing cylinder, especially for calenders and rolling mills

Family Applications Before (1)

Application Number Title Priority Date Filing Date
FR8411041A Pending FR2548929A1 (en) 1983-07-14 1984-07-11 Pressure treatment cylinder, in particular for calanders and laminoirs

Country Status (12)

Country Link
US (1) US4520723A (en)
JP (1) JPH0148410B2 (en)
BR (1) BR8403515A (en)
CA (1) CA1263551A (en)
CH (1) CH664607A5 (en)
DE (1) DE3325385C2 (en)
FI (1) FI76630C (en)
FR (2) FR2548929A1 (en)
GB (1) GB2143302B (en)
NL (1) NL187277C (en)
NO (1) NO162256C (en)
SE (2) SE458386B (en)

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BR8403515A (en) 1985-06-25
FI76630C (en) 1988-11-10
SE458386B (en) 1989-03-20
CA1263551A (en) 1989-12-05
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SE465046B (en) 1991-07-15
FR2548929A1 (en) 1985-01-18
GB2143302A (en) 1985-02-06
CA1263551A1 (en)
JPS6040812A (en) 1985-03-04
CH664607A5 (en) 1988-03-15
SE8803485D0 (en) 1988-09-30
NL187277B (en) 1991-03-01
GB8417182D0 (en) 1984-08-08
DE3325385A1 (en) 1985-01-31
FI842793A0 (en) 1984-07-11
JPH0148410B2 (en) 1989-10-19
FI842793A (en) 1985-01-15
US4520723A (en) 1985-06-04
FI76630B (en) 1988-07-29
DE3325385C2 (en) 1988-11-03
NL8402245A (en) 1985-02-01
NO842876L (en) 1985-01-15
NO162256B (en) 1989-08-21
NO162256C (en) 1989-11-29
SE8403581D0 (en) 1984-07-05
FI842793D0 (en)
GB2143302B (en) 1986-05-29
SE8803485L (en) 1988-09-30
NL187277C (en) 1991-08-01
FR2612430B1 (en) 1993-10-08

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